Fluid supply system with pump operated forced turbulence



May 21, 196s H.-WALD 3,384J64 FLUID SUPPLY SYSTEM WITH PUMP OPRATEDFORCED TURBULENCE Filed Jan. 26, 1965 CON STAHT TOTAL Ill/1111111111United States Patent O 3,384,164 FLUTD SUPPLY SYSTEM WITH PUMP OPERATEDFORCED TURBULENCE Herman Wald, 97-11 Horace Harding Expressway, Queens,N.Y. 11368 Continuation-impart of application Ser. No. 33,237,

June 1, 1960. This application Jan. 26, 1965, Ser.

5 Claims. (Cl. 165-109) This invention relates generally to furtherimprovements in heat `transfer by foro-ed turbulence for pumpappiications. This invention is a continuation-in-part application of myco-pending application Ser. No. 33,237 led J une l, 1960, now abandoned.

The extension of the principles of this invention is concernedespecially, but not exclusively, with liquid operated pumps of any typeor gas operated pumps.

The basic characteristic feature of the invention is of providing twouid displacing channels of equal area to discharge the fluid through aperiodically variable fluid displacing device to produce an oscillatoryshifting of the fluid distribution resulting in a constant totaldischarge in spite of the oscillatory or pulsating delivery through saidrespective individual displacing channels. The pulsating delivery servesthe purpose to substantially destroy the film-layer adhesive between thecontacting surface or mediums.

The importance of said constancy of the instantaneous total dischargethrough both channels lies in the fact that it makes possible aneicient, vibrationless operation of the pump system.

All the pulsating type systems of the present art fail to secure such aninstantaneous constant discharge and are rather concerned with theprovision of two extreme positions of the pulsating or revolving meansso that when one is closed the other shall Open and during theintermediate positions, however, the total discharge is largelyfluctuating, vibrating, or producing a modulating total ow causing avibrating and uneflici-ent operation.

This invention, therefore, has special provision for a dual dischargechannel system allowing to subdivide the discharging total fluid intotwo phase displaced ows and with such a functional variability that aconstant total discharge is secured under any intermediate position ofthe fluid displacing means.

The mentioned revolving means in this application may compriseoscillating fluid-displacing elements having means to vary the cyclingrate or period of oscillation as well as the pulsation-ratio ormagnitude of fluid-pulsations requiring an operation of predeterminedphase-relationship between both fluids flowing into the respectivechannels with simultaneous operation.

The word fluid herein referred to as being pressurefluid means a liquidor gas of higher pressures.

It is, therefore, the main object of the present inn vention to applythe forced-turbulence principle to pumps and is mainly referred to thevarious ldualdischarge methods having a 180 degrees phase-displacementbetween the fluid flows in the respective channels being accomplished byan oscillating duid-displacing means of any preferred reci-procable vaneor piston arrangement for obtaining a continuous constant totaldischarge output in view of securing a vibration-less and eicientoperation of the pump.

This object is mainly accomplished by providing a fluid receiving spacecommunicating with the discharge region of the pump containing twoseparate chambers leading to the respective discharge ports. A movablebody provided with two vanes of predetermined space relationship foroscillating movement such that the fluid-displacing 3,384,164 PatentedMay 21, 1968 ICC vanes are slidably supported and move withreciprocating movement within or along the ports of the chamberscooperating with said moving vanes carried thereby. These sliding vanesoperate in reciprocation for alternately affecting the instantaneousquantity of fluid delivered into the dual channel system. It performsthe function of diS- placing the uid in an oscillatory manner into thedual discharge channels since both vanes upon which the uid pressureacts are subjected to reciprocating movement within and conform to thecontour of the two separate channels.

At one extreme position when the said receiving port of one chamber isin' full communication with the discharge region of the pump, thecorresponding vane aS- sumes a full open position, whereas the othervane assumes a fully closed position with respect to the other port ofthe other chamber. As the fluid-displacing vane system continues Itomove in the slot spaces, the vanes are successively moved out ofcommunication with the said one port of the respective chamber and aresuccessively moved into communication with the second port of thechamber until the full opening position with the second chamber isestablished, thereby t-o become fully filled with the whole fluiddischarge by the pump into the common receiving chamber. As a result, itwill produce an oscillatory shifting of the ow distribution bydisplacing the total ow alternately into the respective dischargechannels since the -two vanes are disposed side by side in fixedspace-relationship and are constrained to move equally and oppositely bythe conventional synchronizing mechanism of the piston type or alikearrangements.

The above described oscillating-uid-displacing means may be adopted toany conventional centrifugal or turbine type pump or compressordischarging the fluid through said displacing means into two separateconduits of equal cross sectional area producing the requiredoscillatory shifting into `the respective discharge conduits.

A still further object of the invention is to produce the necessaryreciprocating movement effecting the desired fluid-displacement means bya magnetic vibrating-plunger actuating same with additional provisionsto vary the pulsation ratio and cycling rate.

It is another specific object of the invention t-o provide adual-discharge pump assembly providing two independent fluid deliveriesof the pulsating character in such a manner as to maintain the totalconstant discharge through both outlets as required for an efficientoperation of the pump system. Such a dual discharge pump assembly isespecially adaptable for using its method of operation in feeding andcooling the combustion chamber of a rocket power plant as it will befully described in connection with this particular application.

According to the above objects of the invention, two oscillatingfluid-displacement devices cooperate with the two separate dischargechannels. However, a plurality of conduits may be employed or arrangedin parallel combination to form two independent group of conduitsconstituting two separate discharge passages of equal total area of eachgroup, thereby to provide the desired oscillatory shifting of the owdistribution into the respective group of conduits. Both groups mayconstitute a heat transfer surface or coil for improving the insidecoeicient of heat transfer by the forced turbulent action of thepulsating uid flowing inside pipes. This may be extended to serve forimproving heat transfer to fluid flowing Outside pipes by using asuitable arrangement of the coil.

Thus it is an additional object to provide a heat exchanger apparatus topromote the overall heat transfer between two iluids being separated bya transfer surface.

This invention possesses many other advantages and has several otherobjects which may be made more easily apparent from a consideration ofsome of the embodiments of the invention. For this purpose there isshown some representative forms in the drawings accompanying and formingpart of the present invention. These forms will be now described indetail, illustrating the general principles of the invention; but it isto be understood that this detailed description is not to be taken in alimiting sense.

To the accomplishment of the foregoing and related ends, said inventionthen comprises the features hereinafter fully described and particularlypointed out in the claims, the devices, combinations and arrangements ofparts hereinafter set forth to form various complete uid supply systemsand also include the various combinations and subcombinations ofelements and their interrelation.

For fuller understanding reference will be made to the drawings, inwhich:

FIGURE 1 is a diagrammatic view of the principal embodiment of theinvention applied to pumps using a fluid-displacing device to providethe oscillatory shifting of the flow distribution into the respectivedual-channel system.

FIGURES 1A, 1B, 1C represent the different phasepositions of thefluid-displacing device.

FIGURE 2 illustrates the plot of the time-displacement diagram of thefluid displacement device.

FIGURE 3 represents a diagrammatic view of an electro-magnetic plungertype driving means to actuate the fluid-displacing device.

FIGURE 4 represents a diagrammatic view of a preferred application ofthe pulsating-dual-discharge pump arrangement to effectively pump liquidfuel combustion agents into the rocket-combustion chamber to providemore eflicient cooling of the walls and also to promote combustionefficiency.

FIGURE 5 is a diagrammatic representation of a general configuration ofthe principles involved herein as applied to a pair or group of parallelconductive means.

FIGURE 6 is a general diagram of a dual-discharge system of theinvention where one of the pulsating discharge flows is recirculatedinto the main inlet or shortcircuited.

FIGURE 7 shows the operating phase-characteristics of two fluidsoperating with forced turbulence on either Side of the transfer surfaceto improve the Overall heat transfer.

FIGURE 8 shows another embodiment of the invention as applied to steamsupply systems with forced turbulence.

Referring more particularly to FIGURE l, there is shown a diagrammaticview of an oscillating fluiddisplacing device generally indicated at 1comprising a receiving chamber 2 being supplied by the pressure fluid 3of any pump system 4 through the conduit 5, a horizontally slidablepiston-vane assembly denoted by reference character 6 is rigidlyconnected with piston rod 11. The opposite sides of the vane-assembly 6are provided with slotted guides adapted to engage slidably the inneredges of the slots 9, 10 slidably supporting the fluid-displacementvaries 7, 8, respectively. The vane assembly 6 is constrained to moveequally and oppositely with respect to the discharging ports 12, 13, bya conventional crank or synchronizing mechanism denoted by referencenumeral 14. The vanes 7, 8 are rigidly secured in a predetermined spacedrelationship with respect to each other to conform to the location ofthe discharge ports 12, 13 and constantly engage the wall of thereceiving chamber 2 during their reciprocation by the piston rod 11. Inthis manner the receiving chamber is constantly in communication withthe discharge ports in a cyclic operation, thereby an oscillatoryshifting of the fluid-flow distribution takes place into the dischargeconduits 15, 16, respectively, being due to the alternate closing andopend ing of the respective discharge ports to be effected by thereciprocation of the vane assembly 6.

Since the constructive feature of the crank-piston mechanism is ratherconventional, therefore need not be dwelt upon in more further detail.So much is to be noted that the piston is reciprocated by theconventional crank arrangement to be driven by any type of driving meansor motor, and the extent of eccentricity determines the length of thestroke as required for the fully actuated fluid-displacement into therespective discharge conduits. In this manner the piston-vane assemblyis rapidly reciprocated and provides an alternate pulsation in the fluidflowing into the respective discharge outlets.

In order to analyze the characteristic of the oscillatingflow-displacement, we determine the motion or displacement of thepiston-vane assembly vs. time as produced by the continuously rotatablecrankshaft. Such a motion may be represented by a harmonic curve asillustrated on the time-displacement diagram shown on FIGURE 2 anddefined by the expression, x=r cos wt as being a cosinusoidal variationwith the time. It is a projection on the x axis taken along the axis ofthe stroke and 0 is the midway between the two extreme positions of thepistonvane assembly 6. Thus during rotation of the crank a pin may slidein a horizontal slot (not shown) so that the vertical displacement x ofthe piston is equal to the vertical projection of the crank. Thus itwill readily be seen that the time required for the piston to make onecomplete oscillation along its paths is the same as that required forthe uniformly rotated crank to make one cornplete revolution. The pointsA, B, C on the curve 17 denote the corresponding positions of thepiston-vane displacements. It is seen that the curve gradually changesfrom minimum to maximum or inverse, thereby the sliding vane assemblyengaged with the crank will be gradually accelerated or deceleratedwithout shock in changing their direction of oscillation and thereforeproduces the desired velocity-fluctuations in the fluid flowingtherethrough.

FIGURES 1A, 1B, 1C represent the different vanedisplacement positionscorresponding to the points A, B, C on the curve 17. FIGURE 1A indicatesthe position A on the curve when the vane-assembly allows the fluid afull communication or opening into the discharge port 12 cooperatingwith vane 7 and fully closed position with discharge port 13. FIGURE 1Crepresents an inverse condition when vane 8 cooperates with dischargeport 13 in a similar manner. FIGURE 1B illustrates the condition at themidpoint G on the curve when both discharge ports are half-way open.

It is clear that due to the predetermined fixed spacing of the varies 7,8 with respect to the cooperating discharge ports 12, 13, they areconstrained to move simultaneously causing an inverse variation/of thefree area of both discharge ports during each cycle of thevane-oscillation. A ccordingly the flow rate of fluid discharged fromthe discharge ports varies from zero to maximum and the other variesinversely. As a result, the sum of the fluid quantities discharging fromboth ports is constant at any time-moment of the fluid-displacementobtained by the simultaneous sliding of both vanes. This is true despiteof the cosinusoidal variation of the vane-displacement vs. time as shownby the curve 17 and dashed line curve 18 Accordingly, the variation ofthe free area through port 12 is at any time proportional to cos wt,whereas through port 13 is proportional to (l-cos wt), thereby we obtaina constant total free passage area through both points at instantaneoustime-moment as desired. It will thus readily be seen that by properlyselecting the design of the crank driving means similar to a cam proleor curvature, any desired time-velocity characteristic could beproduced. In a preferred embodiment, not shown here, the profile mayassume a sine-squared form in which case the profile of an othercooperating crank driving means of the same curvature will produce acos-squared curve when a 90 degrees phase-displacement exists betweenboth driving means. Now if we assume that both sliding varies are drivenby the corresponding driving means, the total instantaneous dischargellow through both ports becomes constant as given by the form:

where C is a factor depending on the rod connections, wt angularvelocity.

The pulsation ratio may preferably be controlled by varying themagnitude of the slots on the sliding vanes 7, 8, whereby theoscillatory flow rate fluctuations of the uid can be made from anyminimum to maximum. Any outside control lever means 19 can be adopted tocarry out this adjustment.

Any driving means to be applied to the crankshaft must have provision tocontrol the cycling-rate as required according to the principles of theinvention to assume any desired functional relationship to fluidvelocity entering the fluid-displacing vanes.

By way of example, the simplest type of driving means would be aseparate motor drive of variable speed type or it may be driven by thepump motor itself using some interconnecting means of variable speedratio as required in accordance with the invention.

By way of example, a preferred application is shown on FIGURE 1 when thefluid-displacing device 1 controls the oscillatory shifting of the flowdistribution of forced turbulent character flowing into the respectivedischarge conduits 15, 16 leading into two independent portions of aheat transfer apparatus 19 comprising two coil arrangements 20, 21. Bothflows after leaving the discharge passages of the transfer surface maybe joined together and recirculated through conduit 22 into pumpinlet 23to be treated again. Thus the sum of the lluid-ows discharged from bothpassages is constant at any instantaneous time-moment and a uniform,pulsation-free flow is returned to the pump inlet. This method secures aquiet and vibration-free, eicient operation of the pump despite of thefluctuating supply into the individual respective conduits. This methodof application being only indicative of but a few of the various ways inwhich the principle of dual-discharge pulsating supply of the inventionmay be employed.

FIGURE 3 represents a diagrammatic view of an electromagnetic plungertype driving means to actuate the fluid-displacing device. It mainlyconsists of a non-magnetic cyclindrical structure generally indicated at37 wherein a hollow magnetic plunger is slidably mounted and carryingrigidly secured therewith the vane-assembly 6 actuated by the rodextension of the plunger. Basically it comprises, in combination, anelectrically actuated vibrating plunger member 38 having disposed on andsurrounded by a solenoid-electromagnet to be actuated by A.C. voltage orilux so that the vbratory movement of the plunger member is effected bythe rapid variation in the direction of the magnetic flux of any givenfrequency.

Accordingly the herein described preferred embodiment comprises aU-shaped electromagnet 39 embedded in insulating material and equippedwith a core 40 having an aperture 41 to allow the sliding back and forthof the plunger. In order to vary the rate of oscillation orreciprocation, the A.C. source may consist of a rectilied D.C. sourcefeeding an electric vibratory-means to produce an alternating flux ofany given self-oscillating frequency or it may consist of a timedcondenser-discharge circuit of any conventional type not shown here, andno further details are given. In the latter case the frequency ofthealternating ux may be controlled by varying either the resistor orthe condenser determining the desired frequency.

It is to be noted that this modified design using an electromagneticmeans to actuate the reciprocating plunger of FIG. 1, is ratherpreferred in `high pressure applications using discharge outlets ofrelatively small cross sectional area necessitating a correspondinglysmall pulsatory displacement of the pulsating plunger to perform therequired oscillatory shifting of the fluid ow into the respective branchconduits or outlets 15, 16 by alternately closing said respectivedischarge ports 11, 12.

The general embodiment of the pulsating dual-discharge supply maypreferably be employed Very eiectively in pumping liquid fuel combustionagents from a separate storage container into the rocket combustionchamber. FIGURE 4 represents a diagrammatic view of such a preferredapplication. Usually a rocket power plant includes a turbine driving thepumps with dual discharge provision generally indicated at 77, however,a sliding vane type is shown for the sake of illustration. With theusual design of the rocket chamber 78, the liquid combustion agents arepumped through spiral grooves 79, 79A formed along the walls S0, 80A,which in turn intercommunicates with the chamber by a plurality ofnozzles 81, 81A symmetrically disposed on opposite sides for the purposeof cooling the wall of the combustion chamber. Similarly along the wallof the auxiliary chamber 76 there are spiral grooves 82, 82A disposedfor the same reasons. Since the rocket chamber itself forms no part ofthe present invention, no further description is deemed necessary.

In this connection, the lprinciples of the invention may be applied togood advantage by pumping the liquid cornbustion agents iiowing throughsaid spiral grooves with 4a special pulsating and Iforced turbulentcharacter having two independent discharge outlets in delivering liquidagents through conduits 83, 83A to both independent symmetrical sides ofthe rocket-chamber and similarly branched-olf conduits 84, 84A to theauxiliary chamber through the respective nozzles disposed on each sideof said chambers. Accordingly, in this application the chamber wallserving as transfer surface is subdivided into two symmetrical sectionsand thus two independent groove arrangements are disposed in accordancewith the invention to employ heat transfer surfaces in two symmetricalparts being subjected to the forced turbulent flow of opposite p'hasewith respect to each other.

Therefore each conduit delivers -oscillatory forced turbulent flow ofthe combustion agents through nozzles on each side, providing aconsiderable increase of the cooling-effect on the walls as beinghigh-ly desired to effect a substantial destruction of the film-layer atthe inner `surfaces of the grooves serving as transfer surface. Also thebranched-off turbulent flow may serve to cool the wall of the `auxiliarychamber by sending the liquid agents through the grooves formed alongits wall.

rPhe supply of the liquid combustion agents into the rocket chamber withpulsating character is especially suitable since it may furthercontribute to increase the combustion efficiency caused by the specialforced turbulent ycharacteristic injected through the nozzles. Inaddition to the foregoing advantages, the combustion efficiency is alsogreatly enhanced by applying a tuned-ignition to the highly turbulentmixture in such a manner that the spark shall always occur at theinstantaneous time-moment of maximum amplitude of the pulsating mixture.This may easily be accomplished and controlled by a synchronizing meansnot shown here Iand driven by the same shaft rotating the pumps. Thecontinuous applicati-on of the spark to the pulsating turbulent mixtureof the combustion agents will produce repeated-detonations for a betteroverall combustion e'liciency.

IFIGURE 5 is a diagrammatic represen-tation of an alternate and generalconfiguration of the principles of the invention as applied to a groupof parallel conductive means in such a manner that each group isconsidered as one independent branch conduit of the dual-dischargesystem. Referring to this figure, there is shown a heat transfer surfacedenoted by reference numeral composed of two groups of parallelconductive means 141, 142. The dual discharge conduits 143, 144 areconnected to the respective inlet of the respective groups, thereby todeliver through each group of conductive means a pulsating fiow offorced turbulent character operating in phase opposition with respect toeach other of said groups. Since all other considerations are lotherwiseidentical to that of the double conduit system, no further descriptionof this embodiment is deemed necessary.

FIGURE 6 is la diagrammatic representation of an alternate configurationand embodiment to be generally applied to all embodiments of the presentinvention employing dual-discharge outlets of forced turbulent andpulsating character. This consists mainly of recirculating the iiuidfiow through one of the discharge conduits 145, 146 into the commonintake 23, shown with dashedlines, in case of one single dischargeconduit is `applied leading into the transfer surface. Thisrecirculation is necessitated for maintaining the desired constant fiowthrough conduits at any instantaneous time-moment as required forefficient operation of the pump system.

The recirculation may be formed through a by-pass 147 inter-connectingsaid outlet to the inlet so as to serve as short-circuit to the commoninlet 23 of the pump. A control valve means 148 is adopted to effectthis cont-rol any time it is desired. Thus one part of the fluid whichwould normally 'be fiown into the other part of the transfer surface, isshort circuited to the common suction inlet. Since the kinetic energy ofthe returning fiow is imparted on the intake fiow providing acorresponding reduction of the necessary pump-energy supply of the totalincoming fiow.

H eut transfer' between two fluids of forced turbulence Generally thevarious apparatus proposed for causing the heat interchange between twoiiuids, liquid or gas, usually require the expenditure of abnormalheating or cooling energy. The rate of heat transfer from one to anotheriiuid depends primarily on the magnitude of contact area, the differencein temperature of Iboth fluids and finally the heat transfercoefficient. The unsatisfactory operation of such heat exchangers isIdue to a large extent to the restriction of the `contact area betweenboth fluids, which in turn limits the manner in which heat or coolingeffects of both fiuids are associated with one another. In anotheraspect, the rate of heat transfer is greatly limited by the film layeradhesive to the inside and outside of the separating transfer surface.In other words, this invention contemplates the destruction of both filmlayers and to provide an efficient overall heat transfer despite oflimited transfer surface or flow rate of any particular application.

It is generally known that the overall heat transfer between two -ffuidsis greatly improved by the application of a counter-flow arrangement asbeing due to the tendency of increasing temperature difference along theoutflow direction. With this thought in the mind this inventioncontemplates the provision for a counter-phase operation of the forcedturbulent fiows at the inside and outside of the separating transfersurface. Accordingly, it is to be assumed that the overall heat transferefficiency is still further enhanced by establishing a predeterminedphaserelationship of both fluids operating in counterflow.

Generally the forced turbulence produces a periodical variation of themomentum transfer perpendicular to the fiow direction followed -by aradial diversion being due to the excess of kinetic energy released witha resulting shock effect to destroy the film-layer. In order to get amaximum instantaneous shock effect destroying the film-layer on eitherside of the transfer surface contacting both fluids in counterow, thementioned momentum transfer shall take place simultaneously. To this endthe maximum velocity in the flow of the fiuid 150 and the minimumvelocity `of the fiow of the fiuid 151 shall take place simultaneouslyas shown on FIGURE 7. With this operation of opposed phasecharacteristic the instantaneous over-all heat transfer coefficient onboth sides of the transfer surface 152 and over-all logarithmic meanstemperature differential will greatly increase, which, in turn, resultsin a proportionate increase of the overall heat transfer effect inaccordance with the general expression for counterfiow given by:

where U1, U2 are the over-all coefficients at the respective ends andAtbAtZ are the over-all temperature differentials at the respective endsand lne is the natural logarithm. As above explained, this expressioncontains products of t at one end and the U at the other end,consequently the overall heat transfer Q is greatly enhanced by thiscounter-phase operation since it causes greater differentials on theabove values resulting in a proportionate increase of the overall heattransfer effect.

This synchronization in the operation is accomplished by an interlockingmeans, not shown here, between the fluid-displacing of both fluid flow.This interlocking means may be set in such a manner as to obtain anydesired phase-relationship. However, it is to be noted that the aboveopposed phase arrangement will give the best heat transfer results.

It is, of couse, to be understood that in practical applications onefluid may represent a liquid flowing inside pipe and a gas ow'ingoutside for heat interchange, or it may represent liquids flowing ineither sides of the transfer surface.

Application to steam supply with forced turbulence FIGURE 8 is adiagrammatic view showing an arrangement as applied to steam supply inIaccordance with the invention. In order to develop forced turbulencewith following velocity fluctuations or pulsations through any type ofsteam generator, it is imperative to produce the required oscillatoryvolume fluctuations at the discharge of the condensate pump as shown inthe diagram.

In accordance with the invention, the oscillating fluid displacingdevice generally indicated at is connected to the discharge line 161 ofthe pump 162 leading to the dual-discharge conduits 163, 164 to beconnected to oppositely located points 165, 166 of the steam-generatorapparatus denoted by the reference character 167. Thereafter thepulsating steam flows into the heat-transfer surface 168 with itscondensation returned to the pump inlet 169 through return conduit 170.The pulsations along the return line will appreciably be damped or somedampening provisions may be employed at the inlet of the pump to allow auniform yback-how to enter into the pump.

In case of two steam generator apparatus operating in parallel, notshown here, each discharge conduit leads to the respective transfersurface 'and both return flows are joined together to form a constanttotal flow to allow a uniform fluid-fiow back into the inlet of the pumpas required for an efficient operation.

It is to ybe understood that in this application, any of thedual-discharge pumps described in this invention may be employed toygood advantage to serve as condensation pump with dual-pulsatingdischarge outlets, thereby the separate fluid-displacing device may beeliminated.

It is further to be noted that in this lapplication we assume a zerovelocity of the condensate at the wall of the heat transfer surface andmaximum velocity at the liquid-vapor interface. However, when thevelocity of the uncondensed vapor is substantial compared with thevelocity of the condensate at the vapor-condensate inter-face, becauseof the friction between vapor and condensate-film, the vapor velocityinfluences appreciably the haar h: 0.9LufAT where k is the thermalconductivity of condensate, p is the density, and A is the latent heatof condensation, uf is the Iabsolute viscosity of condensate.

Thus it may readily be seen that the heat transfer coefficient h ismainly proportional to the factors k, p and A, of the condensate andfilm-condensate, consequently the destruction of this film-condensategreatly promotes the heat transfer by the effect of turbulence caused bythe shock-action of the forced velocity fluctuations in the layer ofcondensate in accordance with the principles of this invention asdescribed in above mentioned copending applications.

The forced turbulence method may also be considered as a promoter sinceit frees the surface from condensate, whereby we obtain a much higherrate of condensation than with a wettable surface that is insulated witha continuous film-condensate.

As further advantages of this forced turbulence may be mentioned thegeneral promotion of condensate-flow, the purging of the system from airand gases and thereby the over-all improvement of the heat-transferefficiency of the whole system.

While in the foregoing there has been shown and described some of thepreferred embodiments of this invention it will, of course, beunderstood that various details of construction, combinations andarrangements of parts may be resorted to without 'departing from theprinciples of the invention including its spirit and scope, it is,therefore, not the purpose to limit the patent granted thereon otherwisethan necessitated by the scope of the appended claims.

What I claim las new and desire to secure by Letters Patent of theUnited States is:

1. A uid supply system with forced turbulence for improving heattransfer rates comprising, a fiuid supply source under pressure, achamber having a uid receiving portion and a fluid discharging portion,

a heat transfer apparatus having a heat transfer surface divided intotwo equal areas,

said uid discharging portion divided into two equal areas communicatingwith respective areas of the divided areas of the heat transfer surface,

said fluid receiving portion communicating with said uid source,

means comprising in part slideable valves positioned in the dividedareas of the discharging portion of the chamber,

said means causing one of the areas of the discharging portion to have aflow area proportional to a sinusoidally varying time function and theother area of the discharging portion to have a flow area proportionalto the co-function (cosine) of the sinusoidally varying time function,

thereby to cause a total flow through said discharging portion of saidchamber which remains constant and also to subject each of the dividedareas of the heat transfer surface to an oscillating fluid flow tosubstantially reduce the thickness of any stagnant film layer at saidsurface.

2. The structure as defined in claim 1 wherein each of the divided areasof said heat transfer surface being Icomposed of a `group of parallelconductive means, each of said divided areas of said fluid dischargingportion communicating with respective areas of said group of parallelconductive means.

3. The structure as defined in claim 1 wherein each of the areas of saiddischarging portion to have Ia flow area proportional to a sine squaredtime function and the other area of said discharging portion to have aflow area proportional to a cosine squared time function.

4. The structure as defined in claim 1 wherein said uid supply sourcecomprising a steam generating apparatus, said heat transfer surfacehaving condensation conductive means disposed therewith., said Ibothdischarge ports being disposed in fluid communication with oppositelylocated points on said steam generating apparatus, thereby to produce apulsating steam supply system to substantially destroy the said filmlayer at said heat transfer surface.

5. The structure as defined in claim 1 wherein the two said areas ofsaid heat transfer surface constituting the respective portions of thecombustion chamber wall of a rocket type power plant, each of saidrespective portions including a group of passageways being in heatexchange relation to said combustion chamber, thereby to deliver througheach said group of passageways a pulsating fluid flow.

References Cited UNITED STATES PATENTS 280,346 7/1883 Canaday 137-625.111,835,557 12/1931 Burke 257-1.5 2,050,597 8/1936 Younger 34-1912,351,163 6/1944 Thomas 257-15 2,514,797 7/ 1950 Robinson 257-732,585,626 2/1952 Chilton 60-35.6 2,960,314 11/1960 Bodine 257-73 FOREIGNPATENTS 562,089 11/ 1957 Belgium.

622,024 6/ 1961 Canada.

846,950 9/ 1960 Great Britain.

MEYER PERLIN, Primary Examiner.

ROBERT A. OLEARY, Examiner.

A. W. DAVIS, JR., N. R. WILSON, Assistant Examiners.

1. A FLUID SUPPLY SYSTEM WITH FORCED TURBULENCE FOR IMPROVING HEATTRANSFER RATES COMPRISING, A FLUID SUPPLY SOURCE UNDER PRESSURE, ACHAMBER HAVING A FLUID RECEIVING PORTION AND A FLUID DISCHARGINGPORTION, A HEAT TRANSFER APPARATUS HAVING A HEAT TRANSFER SURFACEDIVIDED INTO TWO EQUAL AREAS, SAID FLUID DISCHARGING PORTION DIVIDEDINTO TWO EQUAL AREAS COMMUNICATING WITH RESPECTIVE AREAS OF THE DIVIDEDAREAS OF THE HEAT TRANSFER SURFACE, SAID FLUID RECEIVING PORTIONCOMMUNICATING WITH SAID FLUID SOURCE, MEANS COMPRISING IN PART SLIDEABLEVALVES POSITIONED IN THE DIVIDED AREAS OF THE DISCHARGING PORTION OF THECHAMBER, SAID MEANS CAUSING ONE OF THE AREAS OF THE DISCHARGING PORTIONTO HAVE A FLOW AREA PROPORTIONAL TO A SINUSOIDALLY VARYING TIME FUNCTIONAND THE OTHER AREA OF THE DISCHARGING PORTION TO HAVE A FLOW AREAPROPORTIONAL TO THE CO-FUNCTION (COSINE) OF THE SINUSOIDALLY VARYINGTIME FUCNTION, THEREBY TO CAUSE A TOTAL FLOW THROUGH SAID DISCHARGINGPORTION OF SAID CHAMBER WHICH REMAINS CONSTANT AND ALSO TO SUBJECT EACHOF THE DIVIDED AREAS OF THE HEAT TRANSFER SURFACE TO AN OSCILLATINGFLUID FLOW TO SUBSTANTIALLY REDUCE THE THICKNESS OF ANY STAGNANT FILMLAYER AT SAID SURFACE.